Target throwing apparatus



Dec. 25, 1962 H. c. FOSTER TARGET THROWING APPARATUS Original Filed June 16, 1954 9 Sheets-Sheet 1 FIG. I

HVVENTUR? HARRY CLARK FOSTER 8 Dec. 25, 1962 H. c. FOSTER TARGET THROWING APPARATUS 9 Sheets-Sheet 2 Original Filed June 16, 1954 INVENTORI FOSTEIR HARRY CLARK BY ATTORNEY Dec. 25, 1962 H. c. FOSTER 3,070,082

TARGET THROWING APPARATUS Original Filed June.l6, 1954 V 9 Sheets-Sheet 3 INVEN TOR. BYHARRY CLARK FOSTER A TT'ORNE Y Dec. 25, 1962 c, FOSTER 3,070,082

TARGET THROWING APPARATUS Original Filed June 16, 1954 9 Sheets-Sheet 4 FIG.

' INVENTOR. HARRY CLARKFosTER Y ATTORNL'Y Dec. 25, 1962 H. c. FOSTER 3,070,082

TARGET THROWING APPARATUS Original Filed June 16, 1954 9 Sheets-Sheet FIG. 5

I Q as INVENTOR! HARRY CLARK FOSTER BY We, ATTORNEY Dec. 25, 1962 H. c. FOSTER TARGET THROWING APPARATUS 9 Sheets-Sheet 6 Original Filed June 16, 1954 INVENTOR. HARRY CLARK FOSTER BY ATTORNEY Dec. 25, 1962 H. c. FOSTER 3,070,082

TARGET THROWING APPARATUS Original Filed June 16, 1954 9 Sheets-Sheet 7 REAOY-TO-FIRE POSITION OF LOADED TARGET.

INVENTOR. HARRY CLARK FOSTER Y A TTOR NEY Dec. 25, 1962 H. c. FOSTER 3,070,082

TARGET THROWING APPARATUS Original Filed June 16, 1954 9 Sheets-Sheet 8 FIG. 8

w g if 5 JNVENTOR. HARRY CLARK FOSTER BY- W A TTORNEY Dec. 25, 1962 H. c. FOSTER TARGET THROWING APPARATUS Original Filed June 16, 1954 F 9 9 Sheets-Sheet 9 IN VEN TOR. HARRY CLARK FOSTER ATTORNEY 3,070,082 Patented Dec. 25, 1962 Free mazes 1 Claim. c1. m-s

This invention relates to target traps of the type for projecting clay targets or pigeons or the like into the air, and more specifiaclly to a target throwing apparatus suitable for use in the sport of skeet shooting with a target magazine and an automatic target loading and throwing arm cocking mechanism.

This application is a division of copending application, Serial No. 845,215, filed October 8, 1959 which in turn is a division of co-pending application Serial No. 437,- 191, filed June 16, 1954 now US. Letters Patent No. 2,925,812, granted February 23, 1960.

In the art of skeet shooting or the like, in which target throwing traps are positioned both on the left and on the right of the shooting old, it is obviously desirable that the two traps required not be loaded and cocked throughout the game by hand since this requires the continual presence and attention of two operators. Heretofore, various kinds of automatic magazine-loading types of traps devised have used electric motors with a coupling mechanism such as gear reducers, sprockets, chains and clutches together with a target magazine carrying one or more stacks of clay targets. Prior traps of this type are generally cumbersome largely on account of the gear transmission system necessary to transfer the power intermittently from the electric motor. Traps of this type suffer from further disadvantages in that they have an unnecessarily complex magazine feed and are characterized by excessive movement of the stack of targets which results in too much target breakage.

Therefore, it is one of the objects of this invention to provide a target throwing trap having a new and improved mechanism adapted to keep the target trap loaded automatically from a magazine without the need for manual loading and supervision by operators and attendants. Another object is to provide a target throwing trap having a compact mechanism of low inertia and utmost dependability for efilciently transmitting the power required intermittently as desired to throw the target, cock the trap, and control the holding and releasing of the target carrier or throwing arm. A still further object of my invention is to provide a new and improved target throwing machine adaptable for holding a large supply of frangible targets with substantially complete elimination of target breakage. Another object is to provide in a target throwing trap a mechanism for delivering the targets from a magazine to a target throwing mechanism with a minimum of move ment and without excessive impact. Another object is to provide in a target throwing trap means for accomplishing smooth operation throughout the cocking cycle. Yet another object is to provide a new and improved target throwing apparatus for skeet shooting or the like. Other objects, features and advantages of my invention will become apparent from the following description of a preferred embodiment thereof and the accompanying drawing, in which:

FIGURE 1 is a side elevational view of a preferred embodiment of the invention taken at the moment immediately after a target has been thrown;

FIGURE 2 is a plan view of the embodiment of FIG- URE 1;

FIGURE 3 is a fragmentary cross-sectional view in elevation taken on line IIIIII of FIGURE 2; with the arm shown returned to the retracted or cocked position;

FIGURE 4 is a fragmentary cross-sectional elevational view taken on line IV-IV of FIGURE 3 the better to illustrate certain details of the holding, cocking transmission and release mechanism involved;

FIGURE 5 is a fragmentary cross-sectional plan view taken on line V-V of FIGURE 4;

FIGURE 6 is a fragmentary cross-sectional plan view taken on line VI-VI of FIGURE 3;

FIGURE 7 is a partial plan view of the embodiment of FIGURE 1 showing the throwing arm. in cocked position in relationship to the escapement .mechanism and the target feed shelf;

FIGURE 8 is an elevational fragmentary view partly in cross-section taken on line VIIIVIII of FIGURE 7 to better illustrate the structure below the magazine at the throwing arm 5; and

FIGURE 9 is a diagrammatic view of the electric power and control system employed with the embodiment illustrated in FIGURE 1.

In accordance with this invention, there is provided a trap powered by a continuously running motor which engages the trap mechanism through a clutch system to cock a spring, which upon being released rotates the target throwing arm to effect throwing of the target, which is then followed by automatic loading of another target to the throwing arm as the result of continued movement of the mechanism. The sequence of target throwing, cooking of the main spring of the trap, and reloading of the target throwing arm occurs substantially automatically in the apparatus upon release of the target throwing arm by the operator.

The apparatus of this invention may be described generally as comprising a base 1, a frame 2, a gear housing 3, a mainspring housing 4, a target carrier or throwing arm 5, a mainspring 6, and an electric motor 7 which supplies power for cocking the trap. Frame 2, housing 3 and housing 4 are fixed together by any suitable fastening means so as to constitute in effect a single frame. Power is supplied from the continuously operating motor to the cocking mechanism and the holding and the releasing mechanism the latter of which are contained in the gear housing 3. The target carrier or throwing arm 5 is mounted for rotation upon the upper end of a shaft 8 to which is imparted a rotational thrust for throwing the target by means of the mainspring 6 disposed protectively under the mainspring housing 4.

The cocking, holding, releasing and target loading mechanism is a compact unit contained in and associated with the gear housing 3. The motor continuously turns one gear in the epicyclic gear train in the gear housing 3 while the rest of the train may be set into operation to cock the throwing arm intermittently following each throwing operation. In accordance with this invention a portion of the gear train is held stationary while the rest of it is permitted to idle during the time the trap is in cocked position. Upon actuation of the release mechanism the cocking mechanism is adapted to transmit power from the motor throughout the entire gear train at suit able speed reduction through the main shaft 8 to the mainspring 5. The gear train rotates the main shaft 8-to tension the mainspring 5 until the mainspring crank 9 attached to the lower end of shaft 8 is'heyond the out dead center afterwhieh the shaft 8 and carrier arm 5 are turned ahead some further distance without shock to the cooked position whereupon the] carrier is held cocked and the gearing is again set to idle. As the target carrier proceeds to the cocked position, a target is automatically fed to the carrier or throwing arm 5 ready for 3 launching. The target is thrown when the release mechanism is actuated electrically from a remote position.

In order that the elevation at which the targets are ejected may be controlled, there is provided an elevation adjustment screw 10 mounted rotatably but not slidably on frame 2 with respect to the length of the screw or crank shaft, one end of which passes threadedly through a swivel 11 pivotally carried by uprights 12 integral with base 1 and the other end of which is provided with a crank handle 13;

The invention will be better understood from the following more detailed description with reference to the embodiment of the invention illustrated in the drawing.

As is shown most clearly in FIGURES l and 2, the entire trap is mounted upon a base 1 which is provided with means such as holes 14, 15 and 16 the latter two of which are arcuately slotted for attaching the base adjustably to any suitable support and which is also provided with a pair of upright supports 12 upon which there is mounted pivotally the C-frame 2 by means of elevation pivot pin 17 which passes through the upper part of the uprights 12. Frame 2 carries motor 7 and also the gear housing 3. Mounted on the upper arm 13 of G-frame 2 is a right magazine support 26 and a left magazine support 19 to which there is attached by suitable means a lower magazine bracket 21 and an intermediate magazine bracket 22 which in turn carry guide rails 23, 2d and 25. These three guide rails, including rear guide rails 23 and 24 and the front rail 25, define the magazine space for holding a stack of nested targets. Near their upper ends the-rails are attached to an upper magazine bracket 26. Attached to the front of the gear housing 3 is the mainspring housing or apron 4 which protectively covers and also provides a mount for one end of the mainspring 6 which provides the sudden thrust of throwing power needed to project a target in desirable fashion. The other end of the mainspring 6 is attached to the mainspring crank 9 which in turn imparts a rotational thrust to the main shaft 8 passing through the gear housing 3 and journaled at its lower end in the bottom of housing 3. The upper end of main shaft 8 is indirectly journaled through the hub 27 of feed cam 31 in the gear housing cover 29 from which the shaft protrudes sufiiciently to carry the escapement cam 36, the carrier or throwing arm with its other components and target feed cam 31 all by means of a splined fitting 32 at the upper end of the shaft 8.

The target carrier or throwing arm 5 has a carrier plate 33 and a rubber or other resilient material faced rail 34.

The arm '5 is formed with an upward tilt of about 5 as an extension of the circular disc portion 35 which is provided with a hub 36 internally splined at 37 for attachment to the splined fitting 32 of the main shaft 8. At the outer end of arm 5 and supported underneath it is a carrier plate 33 which supports the target in its initial travel during the throwing operation from the moment of firing to the moment when the target leaves the arm. Although plate 33 in this embodiment is attached to arm 5, it is to be understood that plate 33 could be a separate stationary member mounted on frame 2 and of suitable arcuate length to support the target while it is propelled by the rail 34. In this embodiment described, the leading edge of the plate 33 adjacent shelf 126 in cocked position is formed with a projection 175 to prevent interference with the trailing edge of the target in throwing. Depending from the carrier arm 5 is the angularly adjustable rail 34, having the resilient leading edge 37 and which is pivotably attached at the inner end to arm 5 at the fastener 39 to extend outwardly above the carrier plate 33 at least to the slot 40. Angular control of the target trajectory and control of the levelness of the trajectory is attained by angular movement of the adjustable carrier rail 34 about pivot 39 to a desired position of the outer carrier rail support 41 as determined by the position of support fastener 42 in the arcuate slot 40 in the carrier plate 33.

Slot is of such length as to permit the rail 34- to be adjusted to an angle of lead or lag as necessary to correct for the effect of windage on levelness and direction. For example, a lagging rail causes a target discharge to the right with a tendency to a right tilt, whereas a leading rail causes a target discharge to the left with a tendency to a left tilt. To reduce the moment of inertia, the arm 5 is cast of a light metal such as a suitable magnesium alloy or the like and the light metal carrier plate 33, it will be noted from FIGURE 2. in particular, has a number of openings or cut out sections. It is to be noted that the rail 34 is adapted to be reversibly mounted to compensate for wear.

The main power for throwing the target with the sudend impact necessary is supplied at the lower end of the main shaft 8 by mainspring 6, the ends of which are threadedly secured to an adjustable internally threaded mainspring plug 43 at the front end and similarly to a second mainspring plug 44 at the rear for connection to the mainspring crank 9 as shown in FIGURE 3. The rear mainspring plug 44 is pivoted at one end to the crank 9 by means of mainspring crank stud 45 which is rotatable in crank stud bushing 46. The other or front mainspring plug 43 threadedly receives the T-headed mainspring adjusting screw 47 which in turn passes through mainspring swivel block 48 and through a slotted opening 49 in the frame 4. Screw 47 permits adjustment of the mainspring tension. The swivel block 48 permits lateral oscillation of the mainspring 6, without bending the spring. Mainspring 6 is a closely Wound flat metal ribbon coiled edge- Wise, in order to permit a relatively heavy spring to be utilized in a longitudinally small space or length.

The mainspring crank 9 is fixedly attached at its hub to the lower end of the main shaft 3 by means of a key 50 and a clamp screw 51. The main shaft 8, as is shown in FIGURE 4, extends through the bottom of the gear housing 3 and is there rotatably supported in a main shaft lower bearing 52. Mounted in the bottom of the gear housing 3 above this bushing there is a main shaft oil seal 53 disposed between the main shaft 8 and the housing 3 to prevent loss of the oil bath contained in the housing. Upon expenditure of the throwing power stored up in the spring 6 at the conclusion of a target throwing operation,

cocking power is automatically channeled from the continuously operating motor 7 through the flexible coupling 54 (FIGURE 2) and the worm drive shaft 55 to the epicyclic gear train in gear housing 3 by way of the worm wheel gear 56 (FIGURE 5).

In the gear housing 3, worm drive shaft 55 having a worm of sutficiently steep lead to avoid self-locking, is journaled in worm shaft bushings 57 and 58 (FIGURE 5). The worm wheel gear 56 and also the firing ratchet 59 are mounted fixedly by means of key 60 on the hub 61 of the sun gear 62. The hub 61 in turn is rotatably mounted by means of sun gear bushings 63 and 64 on the main shaft 8. Also located in housing 3 is the control cam 65 fixedly mounted by means of the lower splined fitting 66 on the rotatably main shaft 8. Carried on the control cam 65 are the planet studs 67, 78 and 69. Mounted rotatably on these studs are planet gears 70, 71 and 72. Confined between worm wheel gear 56 and control cam 65 and mounted rotatably on a shoulder of the control cam 65 is the internal ring gear 73 with the external ratchet 74. The planet gears 76, 71 and 72 are also in engagement with the sun gear 62 and the ring gear 73. Control cam 65 is provided at its lower end with a cam surface having a protuberant control portion cam surface 75 and a recessed control cam surface 76 generated by a shorter radius than that which generates the protuberant portion 75.

Control cam 65 also has a rim portion 77 in which is formed a holding notch 78 designed for coaction with a sear 79 formed on the lower portion of the sear member 80 which is rotatably carried by shaft 81 journaled in gear housing 3. The upper end of the sear member 80 is provided with an operating arm 82 linked by means of the firing bar stud 83 to one end of firing bar 84 adjacent to the other end of which, resting in slotted end of guide 114, there is provided a firing pawl shoulder or abutment 85 and a control extension 174. This end of the firing bar is adapted to be acted upon by the firing pin 113 slidably carried in firing pin guide 114- mounted on housing under the impetus of plunger 36 of the release solenoid 87 so as to force pawl shoulder 85 into the teeth of the ratchet wheel 59. Extension 174 is a surface limiting the engagement of the shoulder 85 with wheel 59 and thus determines the extent of movement of bar 84. Pressing against the other end of firing bar 34 adjacent the stud 83 and tending to turn the bar 84 about stud 83 counterclockwise (FiGURE 5) against plunger 85, is the sear plunger 86 which is yieldably mounted against the sear spring 39 carried in an extension of the housing 3 known as a sear plunger bushing 9d. Sear plunger 88 also functions through firing bar stud 83 to turn operating lever 82 clockwise so as to urge sear 79 into notch 73.

In order to reduce the weight and moment of inertia of the parts of the trap which turn in unison during the throwing operation so as to obtain the highest proportion of target throwing spring power, it will be noted (FIG- URE 4) that the control cam 65 is almost entirely hollowed out except for three radial ribs each of which carries one of the planetary gears and connects the rim and cam portions of cam 65 to its hub portion. To further reduce its wei ht, the cam 65 may consist of a suitable light metal or alloy.

Also mounted in housing 3 is a cocking pawl 91, the hub 92 of which is pivotally mounted on the eccentric hub 93 of the hold back pawl 94 which in turn is pivotally mounted on and carried by the shaft $5. The upper end of the cocking pawl 91 is provided with a tooth for engagement with the teeth or serrations of the external ratchet 74 carried on the ring gear 73. When the tooth $6 of pawl $1 engages with the ratchet 74, the force of ring gear 73 on the cocking pawl 91 acting through the eccentric hub turns the hold back pawl 94 clockwise into engagement with the ratchet 74 (FIGURE 6). The lower end of cocking pawl 91 carries a follower 97 for engagement with the cam surfaces 75 and 76 of the control cam 65. One side of the end of hold back pawl 94 is also adaptable for engagement with the teeth or serrations of the ratchet 7d of the ring gear 73. Bearing against the back side of the cocking pawl is the cocking pawl spring 93, acting to thrust the cocking pawl 91 away from the wall of the gear housing into or toward both the ring 73 and control cam 65. The other side of the end of hold back pawl 94 is formed to act as an armature seating against a pawl holding permanent magnet 99, which is mounted on a non-magnetic member 1M carried by and extending into housing 3. Magnet 99 is fastened to member 101 by means of a U-shaped strap 1% having limited pivotal movement to aid both poles of magnet 99 to seat on pawl 94. However, the magnet may be rigidly mounted. The structure of the cocking pawl 91 and the hold back pawl 94 is such that in cooperation with the gearing these members prevent undesired acceleration and the shock movement which would result after the mainspring crank stud 45 has passed the out dead center at the conclusion of the cocking operation.

To permit manual operation of the trap for testing or the like, gear housing 3 also contains a trigger dog 102 pivotally mounted by means of trigger arm shaft M3 on gear housing cover 29 and adapted to be turned against the operating arm 32 of the scar member 80 (FIGURE 5), when the handle of the trigger 165 is pulled up (FIG- URE l). Trigger 1% mounted pivotally outside frame 2 acting through the trigger pull rod 106 and the trigger arm 1G7, which is acted upon by compression spring 115 and is disposed above gear housing cover 29 and is attached to the upper end of trigger arm shaft 103 to the lower end of which dog 192 is attached, causes the dog 5 102 to turn counter-clockwise (FIGURE 5) to press against operating arm 82 turning the sear member and its sear 79 counter-clockwise so as to lift sear 79 out of the notch 78 in the rim of control cam 65 (FIGURE 6).

Suitably secured on gear housing 3 is a cover 29 in which hub 27 of tar et feed cam 31, mounted on main shaft 8, is rotatably mounted by means of an upper main bearing 108 (FIGURE 4). Separation of cover 29 and cam 31 is prevented by a feed cam collar 194 secured on the end of the hub 27 of cam 31 by means of feed cam collar pins 23. Target feed cam 31 has a well for receiving the hub of carrier arm 5 so as to permit a greater degree of engagement between arm 5 and main shaft 8 at the splined fitting 32.

As pointed out hereinbefore, the magazine structure consists of three magazine brackets 21, 22 and 26 of U- shape and three guide rails 23, 24 and 25. Although the magazine structure receives primary support from the magazine supports 19 and 26 to which the lower bracket 21 and the intermediate bracket 22 are. attached, further support to minimize vibration is derived through a cylindrical magazine stabilizer body 139 which is connected pivotally but fioatably by means of a pin 11th in a large hole (FIGURES 1 and 3) to the hollowed out forepart of the lower magazine bracket 21. The magazine stabilizer 169 is rotatably connected by means of magazine stabilizer bushing 111 to the upper end of the main shaft 8. The stabilizer 109 rests upon the target escapement cam 3h against which it is urged by stabilizer spring 112 carried in a recess in the forepart of the lower magazine bracket 21. Stabilizer 109 thus also serves to constrain the target escapement cam 34 the carrier arm 5, and to some extent the target feed cam 31 all three of which are in engagement with the splined fitting 32 at the upper end of main shaft 8. It is to be noted that the target feed cam 31 is already constrained axially on main shaft 8 by means of the gear housing cover 29 with the aid of feed cam collar 104 fixed on the end of cam hub 27 by pins 28.

A supply stack 116 of nested targets is carried in the ,magazine between magazine parallel guide rails 23, 24 and 25. At the lower end, rear guide rails 23 and 24- extend below the lower end of front guide rail 25. The space left at the lower end of front guide rail 25 is for entry of a pair of resilient escapement cushions 117 and 118. These cushions are carried between an escapement carrier base 119 and escapement carrier cover plate 120 which forms a sort of cushion carriage capable of slight oscillation as permitted by the clearance between the overhanging edge 121 of escapernent carrier base 119 and the driven arm 122 of the escapement lever 123 upon which the carriage is pivotally mounted about the hub 124. Cushions 117 and 113 are thus adaptable to press against the lowermost target or against the second lowermost target of the supply stack 116, as will be explained hereinafter in connection with the operation of the trap.

Mounted on the feed shelf operating bracket 125 below the magazine is a target feed shelf 126 which coacts with the target feed arm 127 one end of which is pivoted on the gear housing cover 29 and carries rotatably intermediate the ends of arm 127 a feed cam roll 12% mounted on arm 127 by means of stud 129 and bushing 130 (FIGURE 4) which follows the profile of the target feed cam 31 and thereby controls the operation of the target feed shelf by means of feed shelf roll 161. Depending from and attached to bracket 125 are a pair of spaced feed shelf guide rods 130 and 131 which slidably engage with feed shelf guide bushings 132 and 133 which are mounted on and protrude from the upper surface of frame 2 at the feed shelf. Disposed about each bushing and guide rod is a feed shelf lifting spring such as springs 134 and 1,35 mounted in compression between bracket 125 and frame 2. Accurate positioning of the feed shelf 126 is obtained by interposition of feed shelf shims 136 between the shelf 126 and the bracket 125. It is evident that the feed shelf 126 is raised by feed shelf lifting springs 134 and 135 and 7 is lowered by target feed cam 31 in timed relationship with the rotation of carrier arm 5.

Release of the targets from the bottom of the stack in the magazine to shelf 126 is controlled by the escapement mechanism which comprise essentially escapement cushions 117 and 118, the escapement lever 123 pivotally mounted by means of escapement lever stud 137 on the lower magazine bracket 21, the escapement cam roll 138, and the target escapement cam 31 which is carried as stated hereinbefore on the splined fitting 32 at the upper end of main shaft 8.

When the target escapement cam roll 138, rotatably mounted on the end of the driving arm 139 of the escapement lever 123, is opposite the receding portion of target escapement cam 30, lever 123 is free to turn counterclockwise about stud 137 (FIGURES 2 and 7) under the force of escapement tension spring 140, one end of which is connected to the end of the driven arm 122 of lever 123 while the other end of spring 140 is connected to the escapement lever spring post 141 dependently mounted on lower magazine bracket 21, thus forcing resilient cushions 117 and 118 into engagement with the lower rim of a target at the bottom of the stack. This target and all the targets above it are thus secured against dropping by the forces exerted on the target by cushions 117 and 118 and the rear guide rails 23 and 24. When the escapement cam roll 138 rides on the protuberant portion of the cam surface of target escapement cam 30, lever 123 acting against spring 140 has been forced clockwise as far as possible, disengaging cushions 117 and 118 from the stack of targets 116. In this position the stack rests upon and is supported by the target feed shelf 126.

In association with the electrical system which provides both power and control for the trap and which ineluudes the motor 7, there is a release solenoid 87 having a plunger 86 for pushing firing pin 113 slidably carried in the firing pin guide 114 mounted in gear housing 3 to initiate the throwing operation. Solenoid 87 is mounted by suitable fasteners under a solenoid housing 146 provided for convenience with a hand grip 147; and housing 146 in turn is mounted by means of screws 148 and 149 to mainspring housing 4 so as to become in effect a part of frame 2.

The electric wiring system of the trap may be described best with reference to FIGURE 9 for two such identical traps inasmuch as two traps are required for the game of skeet. In the drawing a second wiring system identical with the first is shown in broken lines for a second trap identical with that described herein. The wiring system of the trap itself is all carried within the parts 2, 3 and 4 and is connected to the threepronged power inlet receptacle 143. As shown in the drawing one of the power lines 144 is connected to one side of the motor 7. The other side of the motor 7 is connected to one side of the solenoid 87 and to one side of master switch 145, the other side of which is connected to the other power line 150. The operation of the motor 7 is controlled by means of master switch 145 which is accessibly mounted on the upper arm 18 of C-frame 2 (FIGURES 1 and 2), and which is normally closed during the period of operation of the trap. The other side of the solenoid 87 is connected to the third or control line 151. Power line 144 is connected at receptacle 143 by means of power inlet connector or plug 152 to insulated external power line 153 which leads to a source of power 154 by way of double pole fused disconnect switch 155. The other power line 150 similarly is connected to the other insulated external power line 156 leading from switch 155. Control line 151 similarly is connected at receptacle 143 to line 157 which leads to a special skeet release switch mechanism 158 to which one of the power lines 153 is also connected by insulated lead wire 159. For convenience power lines 153 and 156 and control line 157 located externally of the trap may be all contained in a single insulated cable extending from the power inlet plug 152 to the junction box 160 common to the two traps employed. In like fashion the other trap is electrically connected to the electric power source 154 and to the special skeet release switch mechanism 1158. Switch mechanism 158, connected to wiring in juncion box 161 by a suitable insulated three conductor electric cable, is adapted to operate either one or the other of the traps or both simulataneously at the will of the operator who is located remotely from the positions at which the two traps are located. It is to be noted that when master switch 145 is open, both motor 7 and release solenoid 37 are deactivated. This is a safety feature in that the arm 5 may not then be released by closing control contacts 142 of switch mechanism 158 with a possibility of injury to anyone at the trap.

With the trap in cocked position with a target emplaced upon the carrier arm plate 33 from the stack 116 in the magazine, the target is thrown by momentarily closing the electric contact 142 of the release switch 158 (FEGURE 9), whereupon release solenoid 37 is energized and its plunger 86 pushes firing 113 against the end of firing bar 84 causing firing pawl shoulder or tooth to engage with and be moved to the right by ratchet wheel 59 which is continuously turned counter-clockwise (FIGURE 5). Thus moved, firing bar 54, acting through firing bar stud 83, exerts a force on the end of operating arm or lever 82 of the sear member 50 which as a result is turned to lift the sear 79 out of notch 78 formed in the rim 77 of control cam 65 (FIGURES 3, 4 and 6). This releases the control cam 65, main shaft 8, target feed cam 31, throwing arm 5 and target escapement cam 30- to turn counter-clockwise in unison leaving arm 5 free to throw the target from the carrier plate 33 under the impetus of tensioned mainspring 6 acting from a point at which mainspring crank stud 45 is about 30 following out dead center. During the first part of the target throwing or firing operation, the follower 97 of the cocking pawl 91 rides the proturberant portion 75 of cam 65 holding the cocking pawl tooth 96 from clattering along the teeth of ratchet 74 of ring gear 73 which during firing also turns counter-clockwise in the same direction as arm 5, main shaft 3, and continuously turning sun gear 62 inasmuch as the control cam 6'5 carrying the planetary gears 70, 71 and 72 is turning with main shaft 8 far more rapidly under the impetus of mainspring 6 than the rate at which the platetary gears are caused to turn about planet gear studs 67, 68 and 69 under the impetus of the sun gear 62 driven by the motor 7.

At the beginning and for about the first 50 of the throwing operation target feed cam 31, acting through feed cam roll 128, target feed arm 127, and feed bracket or shelf operating roller 161, holds the target feed shelf 126 at the lower end of its travel at which shelf 126 is in line with the carrier plate 33 of rotating arm 5. At about 50 of the turning cycle of the arm measured from the cocked position, feed cam 31 begins to permit elevation of the feed shelf 126 which at about of rotation arrives at the top position which is slightly below the bottom target of the stack 116. When the arm 5 and cams 30 and 31 arrive at about the mark of angular travel, target escapement cam 30 causes the target escapement cushions 117 and 118 to begin opening. At the position the cushions are retracted and the escapement is fully open and permits the entire stack 116 to drop a slight distance of not more than about of an inch to upraised feed shelf 126'. With the stack 116 thus supported, escapement cam 30 at about the 260 point of angular travel causes the shelf 126 and the stack 116 carried thereon to lower gradually a further distance (about of an inch) equal to slightly less than the height of the rim of one target (about of an inch) so as to position the second target from the bottom of the stack 116 supported on shelf 126 opposite the opened escapement cushions 117 and 118. At this position, which occurs at from about the 280 to about the 300 position of angular travel, escapetnent cam 30 permits the cushions 117 and 118 to close on the target second from the bottom, after which feed shelf cam31 lowers the shelf 126 carrying only a single target by about of an inch to a position in line with the carrier plate 33 to aid in supporting the target just a moment before arm arrives at the loading position below supported stack 116 at a point displaced from cocked and ready-to-fire position by about 15 of angular travel. It is to be noted that the greatest target transfer movement is a movement of but a single supported target and not the entire stack. It is to be further noted that feed shelf 126 in coming up to take down a target from the stack stops just a bit short of meeting with the stack so as not to bump it, which would be likely to break one or more of the frangible targets.

Before target feed shelf 126 is lowered from its elevated position, at about the 250 mark of angular travel of the arm 5, the main shaft 8, as indicated by the position of crank stud 45, has shot beyond in dead center by about 100 and begins to oscillate back or clockwise together with control cam 65. This sudden incipient movement of reversal causes planetary gears 70, 71 and 72 to tend to reverse ring gear 73 and drive it clockwise. But since reversal of ring gear 73 is prevented by the cocking pawl 91, inasmuch as at this position of the parts, follower 97 of the pawl has dropped opposite the receding portion 76 of control cam 65 and permits cocking pawl spring 98 to force tooth 96' of thepawl against ratchet 74 of gear 73, the only action of ring gear 73 is to exert a force on the cocking pawl 91 which causes a torque force on the hold back pawl 94 and brings about clockwise (FIGURE 6) movement of pawl 94 so that it too engages with ratchet 7 of gear 73, which under these circumstances of the mechanism is secured in sta tionary position. With ring gear 73 thus held stationary, rotation of the sun gear 62 causes planetary gears 79, 71 and 72 to move their studs 67, 68 and 69 in the counter-clockwise direction carrying control cam 65, main shaft 8 and the throwing "rm 5 until mainspring crank stud 45 arrives at the out dead center at which position mainspring 6 is fully tensioned. However, at about 15 following out dead center position which corresponds to about 15 of angular movement before throwing arm 5 arrives at the cocked ready-to-fire position, the target carried by descending target feed shelf 126 is picked up by carrier plate 33 and moved along by frictional forces with plate 33. It is to be noted that with the escapement cushions 117 and 118 fully closed upon the lowermost target of those remaining in the stock 116, final descent of target feed shelf 126 has begun at about the 300 position of angular movement of arm 5 and earns 30 and 31, measured from the cocked position.

As soon as stud 45 passes beyond out dead center, the tendency of mainspring 6 in view of the stationary position of ring gear 73, held by pawl 94, is to cause the planetary gears 7 0, 71 and 72 to turn ahead rolling upon the internal teeth of the stationary ring gear 73 faster than motor 7 drives them. As a result, the eifort of mainspring 6 is to drive motor 7 which in turn effects dynamic braking of the main shaft 8 and the arm 5 and the other parts carried on shaft 8. This feature of the mechanism of this invention eliminates the shock which ordinarily would occur just prior to and at placement of arm 5 in cocked ready-to-fire position. Such shock would disrupt the proper positioning of the target on the carrier plate 33.

When the control cam 65 during cocking has been turned to allow sear 79 to fall into notch 78, arm 5 has arrived at the cocked or ready-to-fire position. Here follower 97 has engaged with protuberant portion 75 of cam 65 and has lifted pawl 91 from ratchet 74 of gear 73. This permits gear 73 to turn clockwise again; and as a result of the change in direction, hold back pawl 94 is ejected from ratchet 74. Magnet 99 then engages w'ith' the pawl 94 and keeps itdisengaged from ratchet '74 .until the next cycle.

' It is to be noted (FIGURE 8) that the loaded target on carrier arm 5, just before the arm arrives in the last mentioned position, which is to say the ready-to-fire position, comes into contact with the target feed finger 162 pivotally mounted at 163 on a depending feed finger bracket 164 carried by lower magazine bracket 21. Target feed finger 162 is yieldably held in position by spring 165, one end of which is attached to the feed finger spring post 166 mounted on bracket 164- and the other end of which is attached to one end of the target feed finger 162 which is properly positioned by bearing against feed finger stop 167 also mounted on bracket 164. Feed 162 is adapted to be turned up out of the way when carrier arm 5 is released to project the target. Un til the target, however, is released, feed finger 162 serves to guide the single target against stop finger 163 and target guide button 169 located fixedly on target shelf 126 (FIGURE 7). Stop finger 168 which serves to hold the target in the ready-to-throw position is pivotally mounted by means of pivot 174 on bracket 171 which in turn is mounted on the frame 2. Target stop finger 163 is yieldably held to project upwardly into position by means of spring 172, one end of which is attached to finger 168 while the other is attached to bracket 171. Proper positioning of finger 168 is assured. by a projection 173 from bracket 171(FIGURE 8}. 'It is to be observed that when release switch 142 is closed to cause carrier arm 5 and its plate 33 and rail 34 to go into throwing operation, feed finger 16?; moves up out of the way to clear arm 5 and stop finger 168 is turned down as carrier plate 33 passesover it. Under these circumstances, the loaded target is free to commence movement on plate 33 along rail 34 and be thrown.

When the master switch of the trap is open, in which condition motor 7 is stopped, the trap after firing is inoperable and throwing arm 5 is in the fired position as shown in FIGURES 1 and 2. In this position, mainspring crank stud 45 is standing at the in dead center while within the gear housing 3 the control cam 65 is positioned so as to dispose notch 78 about counterclockwise from the cooked position shown in FIGURE 6. At this condition of the trap, sear 79 is resting upon the rim 77 of the control cam 65 out of notch 78 and at the same time follower 97 of the cocking pawl 91 is disposed beyond the trailing end of the protuberant portion 75 at the leading or initial portion of the recessed portion 76 of the control cam 65 which permits the cocking pawl finger 96 to rest in the ratchet teeth 74 of ring gear 73 under the force of compressed cocking pawl spring 98 while the hold back pawl 94 also rests in the ratchet teeth 74 into which it had been moved during the last previous manual firing operation as the stud 45 began to move back toward in dead center. With the parts of the mechanism thus positioned, it is evident that when the master switch 145 of the trap is closed, the first thing that happens as soon as the motor 7 has gone into continuous operation, is that sun gear 62 acting through planetary gears 70, 71 and 72, rolls the planetary gears, the control cam 65 and the arm 5 counter-clockwise (FIGURE 2) until sear 79 falls into notch 78, just before which time follower 97 on cocking pawl 91 rides up on protuberant portion 75 of control cam 6.5 causing the finger 96 of cocking pawl 91 to be disengaged from ratchet 74 of ring gear 73. This gear 73 then goes into clockwise motion the first effect of which is to throw the hold back pawl 94 toward magnet 99 which serves as a detent keeping hold back pawl 94 out of the ratchet of the idling ring gear 73. It is to be noted that on the first cocking stroke from the fired position, a target is fed from the magazine just as if the arm 5 had previously been cocked and gone through a complete cycle.

From the foregoing description, it is obvious that in accordance with this invention a new and compact electrically operated target throwing apparatus with desirable operating characteristics is provided. The apparatus of this invention has the further advantage of automatic loading of targets from a desirably large supply of them in the magazine without the frequent and constant supervision of an operator. Another advantage of the target throwing trap is that target movement both in the magazine and while in transit from the magazine to the throwing arm is gentle so as to virtually eliminate the danger of target breakage. The trap is characterized by smooth operation so as not to interfere with the proper emplacement of the target on the throwing arm. In the event that a defective target should for any reason break, the magazine and loading arrangement is such as to be selfclearing and will suffer no interference with the target feed operation. It will be noted that with the trap structure provided there is no need for constant adjustment and maintenance since practically all the working parts which carry the load are sealed in the oil bath of the housing and are of a sturdy and dependable mechanical nature. Nevertheless, all desirable adjustments such as that of spring tension and angles are available and easily accomplished in the trap. The trap is adapted to be most easily loaded initially while in the fired position shown in FIGURES 1 and 2, which is the safest, after which targets may be added to the nearly depleted supply stack at infrequent intervals as needed with complete safety and without interrupting the continued operation of the trap. Thus, it is quite apparent that the apparatus of this invention is advantageous in the art of skeet shooting and that the objects and advantages are accordingly accomplished.

Since many other embodiments of this invention may occur to those skilled in the art, it is to be understood the foregoing is intended by way of illustration of a preferred embodiment, and not as a limitation of the scope of the present invention except as set forth in the appended claim.

What is claimed is:

In a target throwing trap having a rotatable throwing arm and a mainspring for moving the arm from a cocked position to the target throwing position, the combination of a motor for operating the trap, a main shaft having secured thereon said throwing arm and a crank conmeeting said shaft to said mainspring, a first gear rotatably mounted about said main shaft and adapted to be continuously driven by said motor, a control wheel mounted on said main shaft to turn with said main shaft, a differential pinion rotatably carried by said control wheel and engaging with said first gear, a second gear rotatably mounted and engaging with said differential pinion, a first member for releasably holding said control wheel stationary and said throwing arm in the cocked position, a second member for holding the second gear stationary when the momentum of the released throwing arm is dissipated thereby permitting the first gear to put the differential pinion into revolution, moving the control wheel so as to drive the throwing arm toward the cocked position, said second gear being adapted to turn in idle motion while said control wheel is held stationary and said control wheel having means to initiate the holding action of said second member when the motion of the control Wheel under the impetus of said mainspring is reversed.

References fitted in the tile of this patent UNITED STATES PATENTS 2,063,284 Winans Dec. 8, 1936 2,078,166 Schwerin Apr. 20, 1937 2,666,424 Foster Jan. 19, 1954 

